Portal axle drive for a drive axle of an electric vehicle

ABSTRACT

A portal axle drive for a vehicle axle of an electric vehicle with driving wheels includes a drive shaft (AN) with an input axis (a) and an output shaft (AB) with an output and wheel axis (b). The input axis (a) and the output axis (b) have an axial or portal offset (c). A first gear stage (Ü 1 ) is arranged between the drive shaft (AN) and the output shaft (AB). In an axial direction, a second gear stage (Ü 2 ) is arranged next to the first gear stage (Ü 1 ) and an engagement device (SE) is arranged next to the second gear stage (Ü 2 ). The first gear stage (Ü 1 ) and the second gear stage (Ü 2 ) are engageable via the engagement device (SE).

CROSS-REFERENCE TO RELATED APPLICATION

The present application is related and has right of priority to GermanPatent Application No. 102020205733.8 filed in the German Patent Officeon May 7, 2020, which is incorporated by reference in its entirety forall purposes.

FIELD OF THE INVENTION

The invention relates generally to a portal axle drive or portal drivefor a drive axle of an electric vehicle with driving wheels, including adrive shaft with an input axis and an output shaft with an output orwheel axis, wherein the input axis and the output axis have an axial orportal offset, and wherein a first gear stage is arranged between thedrive shaft and the output shaft.

BACKGROUND

Portal axle drives for vehicle axles are known. Portal axle drives havea portal offset, i.e., an offset between the drive axle, generally anaxle shaft of the axle differential, and the wheel axle. As a result,either a higher ground clearance is achieved for the vehicle, namely forthe case in which the drive axle is situated higher than the wheel axle,or a lower ground clearance, in particular in the case of low-profilevehicles, when the wheel axle is situated higher than the drive axle.

DE 10 2004 003 649 A1 describes a portal drive, which is also referredto as a portal axle drive, with a planetary gearbox, the ring gear ofwhich includes an inner toothing as well as an outer toothing. The inputis formed by the sun gear and/or the sun gear shaft, and the outputtakes place via an output gearwheel, which engages into the outertoothing of the ring gear. The axes of the sun gear shaft and of theoutput gearwheel have a vertical and a horizontal axial offset (portaloffset).

DE 30 27 806 C2 describes a further embodiment of a portal axle drive,namely for a drive axle of a bus. The input of the portal drive takesplace via an axle shaft of the axle differential, which is arrangedoff-center on the axle. The portal drive includes an input pinion drivenby the axle shaft and an output gearwheel, which is arranged over theinput pinion in the vertical direction and the axis of which correspondsto the wheel axis. Between the input pinion and the output gearwheel,two intermediate gearwheels are symmetrically arranged, which are eachin mesh with the input pinion as well as with the output gearwheel. Thisknown portal axle drive has a vertical portal offset, wherein the wheelaxis is arranged above the input axis and, therefore, is suitable, inparticular, for low-profile vehicles.

One problem associated with known vehicle axles driven by an electricmachine is that either the achievable speed range is too low or thedrive torque and/or the tractive force available at the drive axleare/is too low.

BRIEF SUMMARY OF THE INVENTION

Example aspects of the present invention provide a sufficiently high topspeed and grade climbing ability for the vehicle having an electricallydriven vehicle axle with a portal axle drive, i.e., having a portalaxle, in particular for low-profile vehicles.

According to example aspects of the invention, the portal axle driveincludes two gear stages, which are designed as portal stages with anaxial or portal offset, are arranged next to each other, and areengageable via an engagement device. This yields the advantage that twogears are engageable with the portal axle drive according to exampleaspects of the invention, as the result of which, on the one hand—in thesecond gear—a higher top speed and, on the other hand—in the firstgear—a higher tractive force are achievable. The engagement device isarranged directly alongside the two gear stages, i.e., outside of andnot within the two gear stages. This yields a compact design for theportal axle drive. An electric vehicle is understood to be a vehicle, inparticular a low-profile vehicle, which is either driven exclusivelyelectrically, for example, by one or multiple electric machine(s), orincludes a hybrid drive with an internal combustion engine and anelectric machine.

According to a preferred example embodiment, both gear or portal stageseach include an input pinion, an output gearwheel, and intermediategearwheels, which are in mesh with the input pinion as well as with theoutput gearwheel. Therefore, on the one hand, a portal offset and, onthe other hand, a power distribution via the two intermediate gearwheelsare achieved. The input pinions are designed as fixed gears and theoutput gearwheels are designed as idler gears, which are rotatablyarranged on the output shaft.

According to a further preferred example embodiment, the outputgearwheel of the second gear stage, the second output gearwheel, isrotatably arranged on the output gearwheel of the first gear stage, thefirst output gearwheel. This yields the advantage that the first outputgearwheel as well as the second output gearwheel are easily coupleablewith the engagement device arranged alongside the second outputgearwheel. Installation space is therefore saved in the axial direction.

According to a further preferred example embodiment, the outputgearwheel of the first gear stage includes a neck, which acts as abearing base for the output gearwheel of the second gear stage.Simultaneously, a connection to the engagement device is created by theneck, which is designed as a hollow shaft and transmits the torque.

According to a further preferred example embodiment, the first outputgearwheel includes a first driving toothing and the second outputgearwheel includes a second driving toothing, while the engagementdevice includes a synchronizer sleeve with corresponding drivingtoothings. It is therefore ensured that either the first drivingtoothing or the second driving toothing can be brought into engagementwith the corresponding driving toothing of the synchronizer sleeve.Thus, a first gear and a second gear are engageable.

According to a further preferred example embodiment, the engagementdevice is hydraulically or pneumatically actuatable. In the process, thesynchronizer sleeve is displaced into a particular engagement positionby a shifting force generated by the hydraulic or pneumatic pressure.

According to a further preferred example embodiment, the engagementdevice includes an axially displaceable hydraulic piston, which is actedupon by a hydraulic medium or fluid and is kinematically coupled to thesynchronizer sleeve. The movement of the hydraulic piston in the axialdirection is therefore transmitted onto the synchronizer sleeve, whichbrings about a coupling or decoupling of the idler gears.

According to a further preferred example embodiment, the synchronizersleeve is arranged on the output shaft in a rotationally fixed, althoughaxially displaceable, manner. Preferably, this arrangement can beimplemented by a driving toothing or spline. Therefore, the torque ofthe idler gears can be transmitted onto the output shaft via thesynchronizer sleeve.

According to a further preferred example embodiment, the output shaft isdrivingly connected to a planetary gear set. Preferably, the outputshaft of the portal axle drive drives the sun gear shaft of theplanetary gear set, wherein the ring gear shaft of the planetary gearset is fixed or held in place, i.e., supported against the housing. Theoutput of the planetary gear set takes place via the carrier shaft ontothe driving wheel of the vehicle.

According to a further preferred example embodiment, the driven carriershaft of the planetary gear set is integrated into a wheel hub of adriving wheel, i.e., the carrier shaft is part of the wheel hub and,thereby, drives the driving wheel.

According to a further preferred example embodiment, the vehicle axleincludes a housing and a hub carrier fixedly connected to the housing,in which the two gear or portal stages and the engagement device withthe hydraulic piston are arranged. The portal axle drive can thereforebe accommodated in the housing and in the hub carrier compactly andclose to the wheel.

BRIEF DESCRIPTION OF THE DRAWINGS

An exemplary embodiment of the invention is represented in the drawingand is described in greater detail in the following, wherein furtherfeatures and/or advantages can result from the description and/or thedrawing, in which:

FIG. 1 shows a transmission diagram of the portal axle drive accordingto example aspects of the invention for an electrically drivable vehicleaxle;

FIG. 2 shows a structural embodiment of the portal axle drive with thetransmission layout according to FIG. 1 ;

FIG. 3 shows an enlarged partial section of the portal axle drive withan engagement device;

FIG. 4 shows an axial section in the area of the intermediate gears ofthe portal axle drive;

FIG. 5 shows a view in the axial direction toward the first gear stagewith intermediate gears; and

FIG. 6 shows a view toward the second gear stage with intermediategears.

DETAILED DESCRIPTION

Reference will now be made to embodiments of the invention, one or moreexamples of which are shown in the drawings. Each embodiment is providedby way of explanation of the invention, and not as a limitation of theinvention. For example, features illustrated or described as part of oneembodiment can be combined with another embodiment to yield stillanother embodiment. It is intended that the present invention includethese and other modifications and variations to the embodimentsdescribed herein.

FIG. 1 shows a transmission diagram 1, i.e., a schematic of a portalaxle drive PO according to example aspects of the invention, and aplanetary gear set PS, which is drivable by the portal axle drive PO.The portal axle drive PO is preferably utilized for the propulsion of anelectric vehicle, in particular an electrically driven low-profilevehicle. The portal axle drive PO includes a drive shaft AN with aninput axis a and an output shaft AB with an output axis b, which isidentical to the wheel axis b. The input axis a and the output axis b,which is arranged above the input axis a in the drawing and in thevehicle, have a center distance c, which is also referred to as an axialor portal offset c. The drive shaft AN can be driven (not represented)by an axle shaft of an axle differential of the vehicle. The portal axledrive PO has two gear stages, a first gear stage Ü1 and a second gearstage Ü2, which are engageable by an engagement device SE. The firstgear stage Ü1 includes a first gearwheel Z1 (also referred to as a fixedgear Z1) arranged on the drive shaft AN in a rotatably fixed manner anda second gearwheel Z2 (also referred to as an idler gear Z2) rotatablyarranged on the output shaft AB. As is apparent from the drawing, thefirst gearwheel Z1 and the second gearwheel Z2 are not in mesh with eachother in the plane of the drawing. Rather, a gap s1 has been leftbetween the two gearwheels Z1, Z2. The power transmission from thedriving first gearwheel Z1 onto the driven second gearwheel Z2 takesplace via two intermediate gears arranged in front of and behind theplane of the drawing, which are in mesh with the first gearwheel Z1 aswell as with the second gearwheel Z2; a split of the power flow takesplace as a result. A view in the axial direction toward the first gearstage Ü1 with the intermediate gears ZR1, ZR2 is represented in FIG. 5and explained in greater detail with reference thereto. The second gearstage Ü2 includes a third gearwheel Z3 (also referred to as a fixed gearZ3) arranged on the drive shaft AN in a rotatably fixed manner and afourth gearwheel Z4 (also referred to as an idler gear Z4) rotatablyarranged opposite the second gearwheel Z2. Similarly to the first gearstage Ü1, the driving third gearwheel Z3 and the driven fourth gearwheelZ4 are not directly in mesh with each other. Rather, a gap s2 has beenleft between the two gearwheels Z3, Z4 in the plane of the drawing. Thepower flow in the second gear stage Ü2 also takes place, similarly tothe first gear stage Ü1, via the intermediate gears ZR3, ZR4 arranged infront of and behind the plane of the drawing, which are represented inFIG. 6 and explained with reference thereto. Via the engagement deviceSE, which includes a synchronizer sleeve (without a reference character)displaceable in the axial direction, the drive shaft AN can be connectedto the output shaft AB either via the first gear stage Ü1 or via thesecond gear stage Ü2. During the engagement of the first gear stage Ü1,the synchronizer sleeve is in the engagement position A. During theengagement of the second gear stage Ü2, the synchronizer sleeve is inthe engagement position B. Via the synchronizer sleeve, a rotationallyfixed connection is established either between the second gearwheel Z2or between the fourth gearwheel Z4 and the output shaft AB. In a neutralposition N, which is arranged between the two engagement positions A, B,no torque is transmitted between the drive shaft AN and the output shaftAB. It is pointed out that the engagement device SE is not locatedbetween the idler gears Z2, Z4, but rather outside thereof, namelyadjacent to the fourth gearwheel Z4, which is mounted on a hollow shaft(without a reference character) of the second gearwheel Z2. Theplanetary gear set PS includes a sun gear shaft SO, a carrier shaft ST,a ring gear shaft HR supported against or fixed to the housing, andplanetary gears PL mounted on the carrier shaft ST, which are in meshwith the sun gear of the sun gear shaft SO and the ring gear of the ringgear shaft HR. The planetary gear set PS is driven via the sun gearshaft SO by the output shaft AB of the portal axle drive PO. The outputof the planetary gear set PS takes place via the carrier shaft ST, whichcan be integrated into the wheel head of a driving wheel of the vehicle.

FIG. 2 shows a structural embodiment 2 of the transmission diagram 1according to FIG. 1 . Identical reference characters are utilized forfunctionally identical or similar parts. The drive shaft AN, on whichthe fixed gears Z1, Z3 are arranged, has an axial or portal offset cwith respect to the output shaft AB, on which the idler gears Z2, Z4 aremounted, wherein the input axis a is arranged below the output or wheelaxis b in the drawing and also in the vehicle. The gearwheel pair Z1, Z2forms the first gear stage Ü1 and the gearwheel pair Z3, Z4 forms thesecond gear stage Ü2 of the portal axle drive PO. Both gear stages Ü1,Ü2 are engaged via the engagement device SE. The portal axle drive PO isrepresented enlarged in FIGS. 3, 4 and is described in detail withreference thereto. The output shaft AB is mounted in a housing 3 and ahub carrier 4 and is rotationally fixed, at the end face, to the sungear shaft SO of the planetary gear set PS. A sun gear 5 is arranged onthe sun gear shaft SO. The carrier shaft ST, which is integrated into awheel head or wheel hub 6, includes planetary gear journals 7, on whichplanetary gears PL are mounted. The ring gear shaft HR is supportedopposite the hub carrier 4 in a rotationally fixed manner. The wheel hub6, in which the planetary gear set PS is accommodated, is mountedopposite the hub carrier 4 via a tapered roller bearing 8. A drivingwheel (not represented) of the electric vehicle is secured on the wheelhub 6 by wheel bolts 9. A brake disk 10 is rotationally fixed to thewheel hub 6.

FIG. 3 shows an enlarged representation of the portal axle drive PO, ofthe type previously represented in FIG. 2 . Identical referencecharacters are utilized for identical parts. The output shaft AB ismounted opposite the housing 3 at the end via a cylindrical rollerbearing 11. The idler gear Z2, which includes a neck 12 designed as ahollow shaft, is mounted on the output shaft AB via needle bearings 13opposite the output shaft AB. The idler gear Z4 is mounted on the neck12 of the idler gear Z2 by means of further needle bearings 14. The neck12 of the idler gear Z2 includes a first driving toothing 15 (outertoothing) and the idler gear Z4 includes a second driving toothing 16(inner toothing). The engagement device SE includes a synchronizersleeve 17, which is arranged on the output shaft AB in a rotationallyfixed, although axial displaceable, manner via an inner toothing 17 adesigned as driving toothing, and includes an outer toothing 17 bdesigned as driving toothing. In the representation according to FIG. 3, the synchronizer sleeve 17 is in a neutral position, in which thesynchronizer sleeve 17 is held by a fixing pin 18. No torque istransmitted in the neutral position. The synchronizer sleeve 17 isactuated, i.e., displaced into the two engagement positions A, B (FIG. 1), by a hydraulic piston 19, which is axially displaceably arranged in acylindrical bore 20. The hydraulic piston 19 has a first, larger pistonarea 19 a and a second, smaller piston area 19 b, which can be actedupon by a pressure medium, preferably a hydraulic fluid.

In order to engage the first gear, i.e., the first gear stage Ü1, thesynchronizer sleeve 17, which is also referred to as a gear changesleeve 17, is displaced toward the right (in the drawing) by thehydraulic piston 19, and so the inner toothing 17 a of the synchronizersleeve 17 engages into the outer toothing 15 of the idler gear Z2 andestablishes a rotationally fixed, form-locking connection. In order toengage the second gear, i.e., the second gear stage Ü2, the gear changesleeve 17 is displaced toward the left (in the drawing), past theneutral position, and so the outer toothing 17 b of the gear changesleeve 17 engages into the inner toothing 16 of the idler gear Z4.

FIG. 4 shows an axial section in the plane of the input axis a, the axesm1, m2, the intermediate gears ZR1, ZR2 of the first gear stage Ü1, andthe axes m3, m4 of the intermediate gears ZR3, ZR4 of the second gearstage Ü2. In the plane of the drawing, the first gearwheel Z1 is meshedwith the first intermediate gear ZR1 and the second intermediate gearZR2; the third gearwheel Z3 is meshed with the two intermediate gearsZR3, ZR4.

FIG. 5 shows a 3D representation with a view in the direction of thedrive axle AN toward the first gear stage Ü1 with a driving firstgearwheel Z1, the two intermediate gears ZR1, ZR2, and the driven secondgearwheel Z2. It is apparent from this representation that the poweroutput by the driving first gearwheel Z1 is distributed onto the twointermediate gears ZR1, ZR2 and, by these, is transmitted onto thedriven second gearwheel Z2. Due to this power distribution, the toothsystems and the shaft bearings are loaded to a lesser extent.

FIG. 6 shows a 3D representation similar to that in FIG. 5 , althoughwith a view toward the second gear stage Ü2, which is formed by thedriving third gearwheel Z3, the two intermediate gears ZR3, ZR4, and thedriven fourth gearwheel Z4. In comparison to FIG. 5 , the differentdiameter proportions for the first gear stage Ü1 and the second gearstage Ü2 are readily apparent.

Modifications and variations can be made to the embodiments illustratedor described herein without departing from the scope and spirit of theinvention as set forth in the appended claims. In the claims, referencecharacters corresponding to elements recited in the detailed descriptionand the drawings may be recited. Such reference characters are enclosedwithin parentheses and are provided as an aid for reference to exampleembodiments described in the detailed description and the drawings. Suchreference characters are provided for convenience only and have noeffect on the scope of the claims. In particular, such referencecharacters are not intended to limit the claims to the particularexample embodiments described in the detailed description and thedrawings.

REFERENCE CHARACTERS

-   1 transmission diagram-   2 structural embodiment-   3 housing-   4 hub carrier-   5 sun gear-   6 wheel hub-   7 planetary gear journal-   8 tapered roller bearing-   9 wheel bolt-   10 brake disk-   11 cylindrical roller bearing-   12 neck of the second gearwheel-   13 needle bearing-   14 needle bearing-   15 first driving toothing (Z2)-   16 second driving toothing (Z4)-   17 synchronizer sleeve/gear change sleeve-   17 a inner driving toothing-   17 b outer driving toothing-   18 fixing pin-   19 hydraulic piston-   19 a first piston area-   19 b second piston area-   20 cylindrical bore-   A first engagement position-   a input axis-   AB output shaft-   AN drive shaft-   B second engagement position-   b output and wheel axis-   c portal offset-   HR ring gear shaft-   m1 axis (ZR1)-   m2 axis (ZR2)-   m3 axis (ZR3)-   m4 axis (ZR4)-   N neutral position-   PL planetary gear-   PO portal axle drive-   PS planetary gear set-   s1 gap-   s2 gap-   SE engagement device-   SO sun gear shaft-   ST carrier shaft-   Ü1 first gear stage-   Ü2 second gear stage-   Z1 first gearwheel (fixed gear)-   Z2 second gearwheel (idler gear)-   Z3 third gearwheel (fixed gear)-   Z4 fourth gearwheel (idler gear)-   ZR1 first intermediate gear-   ZR2 second intermediate gear-   ZR3 third intermediate gear-   ZR4 fourth intermediate gear

The invention claimed is:
 1. A portal axle drive for a vehicle axle ofan electric vehicle with driving wheels, comprising: a drive shaft (AN)with an input axis (a); an output shaft (AB) with an output and wheelaxis (b), the input axis (a) and the output axis (b) have a portaloffset (c); a first gear stage (Ü1) arranged between the drive shaft(AN) and the output shaft (AB); a second gear stage (Ü2) arranged nextto the first gear stage (Ü1) in an axial direction; and an engagementdevice (SE) arranged next to the second gear stage (Ü2) in an axialdirection, the first gear stage (Ü1) and the second gear stage (Ü2)engageable via the engagement device (SE), wherein each of the firstgear stage (Ü1) and the second gear stage (Ü2) include an input pinion(Z1, Z3), an output gearwheel (Z2, Z4), and two intermediate gears (ZR1,ZR2, ZR3, ZR4), wherein the input pinions (Z1, Z3) of the first andsecond gear stages (Ü1, Ü2) are configured as fixed gears on the driveshaft (AN), wherein the output gearwheels (Z2, Z4) of the first andsecond gear stages (Ü1, Ü2) are configured as idler gears on the outputshaft (AB), and wherein the output gearwheel (Z4) of the second gearstage (Ü2) is rotatably arranged on the output gearwheel (Z2) of thefirst gear stage (Ü1).
 2. The portal axle drive of claim 1, wherein theoutput gearwheel (Z2) of the first gear stage (Ü1) comprises a neck(12), and the output gearwheel (Z4) of the second gear stage (Ü2) ismounted on the neck (12).
 3. The portal axle drive of claim 1, wherein:the output gearwheel (Z2) of the first gear stage (Ü1) has a firstdriving toothing (15); the output gearwheel (Z4) of the second gearstage (Ü2) has a second driving toothing (16); the engagement device(SE) comprises a synchronizer sleeve (17) with corresponding drivingtoothings (17 a, 17 b); and either a first gear or a second gear isengageable by meshing the first driving toothing (15) or the seconddriving toothing (16) with the corresponding driving toothings (17 a, 17b) of the synchronizer sleeve (17).
 4. The portal axle drive of claim 3,wherein the engagement device (SE) is hydraulically or pneumaticallyactuatable.
 5. The portal axle drive of claim 4, wherein the engagementdevice (SE) comprises an axially displaceable hydraulic piston (19)coupled to the synchronizer sleeve (17).
 6. The portal axle drive ofclaim 3, wherein the synchronizer sleeve (17) is arranged on the outputshaft (AB) in a rotationally fixed and axially displaceable manner. 7.The portal axle drive of claim 1, wherein the output shaft (AB) isdrivingly connected to a planetary gear set (PS).
 8. The portal axledrive of claim 7, wherein the planetary gear set (PS) comprises a sungear shaft (SO) drivable by the output shaft (AB), a ring gear shaft(HR) fixed in place, and a driven carrier shaft (ST).
 9. The portal axledrive of claim 8, wherein the carrier shaft (ST) is integrated into awheel hub (6) of a driving wheel.
 10. The portal axle drive of claim 1,wherein the vehicle axle comprises a housing (3) and a hub carrier (4),and the first and the second gear stages (Ü1, Ü2) and the engagementdevice (SE) with a hydraulic piston (19) are arranged within the housing(3) and the hub carrier (4).